US20040007846A1 - Torsion beam suspension - Google Patents
Torsion beam suspension Download PDFInfo
- Publication number
- US20040007846A1 US20040007846A1 US10/313,952 US31395202A US2004007846A1 US 20040007846 A1 US20040007846 A1 US 20040007846A1 US 31395202 A US31395202 A US 31395202A US 2004007846 A1 US2004007846 A1 US 2004007846A1
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- US
- United States
- Prior art keywords
- spindle
- support plate
- spindle support
- trailing arm
- torsion beam
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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- 239000000725 suspension Substances 0.000 title claims description 14
- 238000003466 welding Methods 0.000 abstract description 19
- 238000003754 machining Methods 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 230000015556 catabolic process Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G21/00—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces
- B60G21/02—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected
- B60G21/04—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically
- B60G21/05—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected mechanically between wheels on the same axle but on different sides of the vehicle, i.e. the left and right wheel suspensions being interconnected
- B60G21/051—Trailing arm twist beam axles
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G3/00—Resilient suspensions for a single wheel
- B60G3/02—Resilient suspensions for a single wheel with a single pivoted arm
- B60G3/12—Resilient suspensions for a single wheel with a single pivoted arm the arm being essentially parallel to the longitudinal axis of the vehicle
- B60G3/14—Resilient suspensions for a single wheel with a single pivoted arm the arm being essentially parallel to the longitudinal axis of the vehicle the arm being rigid
- B60G3/145—Resilient suspensions for a single wheel with a single pivoted arm the arm being essentially parallel to the longitudinal axis of the vehicle the arm being rigid the arm forming the axle housing
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G7/00—Pivoted suspension arms; Accessories thereof
- B60G7/008—Attaching arms to unsprung part of vehicle
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2200/00—Indexing codes relating to suspension types
- B60G2200/20—Semi-rigid axle suspensions
- B60G2200/21—Trailing arms connected by a torsional beam, i.e. twist-beam axles
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2200/00—Indexing codes relating to suspension types
- B60G2200/40—Indexing codes relating to the wheels in the suspensions
- B60G2200/42—Driven wheels or dead axles
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/10—Type of spring
- B60G2202/13—Torsion spring
- B60G2202/136—Twist-beam type arrangement
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
- B60G2204/10—Mounting of suspension elements
- B60G2204/12—Mounting of springs or dampers
- B60G2204/124—Mounting of coil springs
- B60G2204/1246—Mounting of coil springs on twist beam axles
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
- B60G2204/10—Mounting of suspension elements
- B60G2204/14—Mounting of suspension arms
- B60G2204/148—Mounting of suspension arms on the unsprung part of the vehicle, e.g. wheel knuckle or rigid axle
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
- B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
- B60G2206/012—Hollow or tubular elements
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
- B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
- B60G2206/20—Constructional features of semi-rigid axles, e.g. twist beam type axles
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
- B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
- B60G2206/30—Constructional features of rigid axles
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
- B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
- B60G2206/50—Constructional features of wheel supports or knuckles, e.g. steering knuckles, spindle attachments
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
- B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
- B60G2206/70—Materials used in suspensions
- B60G2206/72—Steel
- B60G2206/722—Plates
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
- B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
- B60G2206/80—Manufacturing procedures
- B60G2206/81—Shaping
- B60G2206/8102—Shaping by stamping
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2206/00—Indexing codes related to the manufacturing of suspensions: constructional features, the materials used, procedures or tools
- B60G2206/01—Constructional features of suspension elements, e.g. arms, dampers, springs
- B60G2206/80—Manufacturing procedures
- B60G2206/82—Joining
- B60G2206/8201—Joining by welding
Definitions
- the present invention relates to a torsion beam suspension comprising: vertically pivotable left and right trailing arms extending in a longitudinal direction of a vehicle body; a torsion beam extending in a lateral direction of the vehicle body, the opposite ends of which are connected to the left and right trailing arms; a spindle support plate welded to each of the left and right trailing arms; and a spindle fixed to the spindle support plate so as to axially support a wheel.
- a conventional torsion beam suspension is known from Japanese Patent Application Laid-open No. 2000-94917.
- a trailing arm is a hollow member made by combining and integrally welding press-formed upper and lower plates, and a bracket formed from an angular U-shaped metal plate is welded to the trailing arm to secure a spindle support plate which supports a wheel.
- the above-mentioned conventional design has a problem in that the spindle axle line and the trailing arm major cross-section are largely offset with the angular U-shaped bracket disposed therebetween, so that the bracket must have a wall thick enough to reliably support a load from the wheel, resulting in an increased weight.
- the spindle support plate can be machined to be flat and thinner after welding the spindle support plate to the trailing arm end.
- the spindle axle line is the reference for the surface cut, it is necessary to rotate the whole trailing arm in conducting the surface cut, so that machining becomes very complicated and costly.
- an object of the present invention is to reduce weight by reducing the wall thickness of the spindle support plate which is directly welded to the end of the trailing arm, and to effectively prevent thermal warp which accompanies welding.
- a torsion beam suspension comprising: vertically pivotable left and right trailing arms extending in a longitudinal direction of a vehicle body; a torsion beam extending in a lateral direction of the vehicle body, the opposite ends of which are connected to the left and right trailing arms; a spindle support plate welded to each of the left and right trailing arms; and a spindle fixed to the spindle support plate so as to axially support a wheel, wherein a bent flange is formed around an outer periphery of a body of the spindle support plate and is fitted around an outer periphery of an end of the trailing arm, the bent flange being welded to the trailing arm.
- a spindle support hole is formed in the body of the spindle support plate by burring, and the spindle is press-fitted into the spindle support hole.
- the spindle support hole can be formed in the spindle support plate by burring because the spindle support plate is made thinner.
- the spindle can be retained by press-fitting it into the burring-formed spindle support hole without forming a spindle-mounting flange assembly to retain the spindle support plate, that is, the spindle weight can be reduced by the weight of the eliminated mounting flange.
- a tip end of the spindle press-fitted into the spindle support hole passes through within the trailing arm and projects out of the trailing arm, a projecting portion of the spindle being welded to the trailing arm.
- FIG. 1 is a front plan view of the left half of a torsion beam suspension.
- FIG. 2 is an enlarged cross-sectional view taken along line 2 - 2 in FIG. 1.
- FIG. 3 is a cross-sectional view taken along line 3 - 3 in FIG. 1.
- FIG. 4 is a cross-sectional view taken along line 4 - 4 in FIG. 2.
- FIG. 5 is a view taken from arrow 5 in FIG. 3.
- FIG. 1 is a front plan view of the left half of a torsion beam suspension for rear wheels of an automobile, and the right half of the torsion beam suspension has a construction symmetrical with that of left half with respect to the longitudinal centerline of the vehicle.
- the torsion beam suspension has left and right trailing arms 10 , 10 which extend in the longitudinal direction of a vehicle body, and torsion beam 11 which extends in the lateral direction of the vehicle body to link to the left and right trailing arms 10 , 10 .
- the front end of the trailing arm 10 is welded to a tubular trailing arm support 12 .
- the trailing arm 10 is vertically pivotably supported on the vehicle body via a rubber bushing joint (not shown) accommodated in the trailing arm support 12 .
- a rear wheel W is rotatably supported on the spindle 14 fixed to the spindle support plate 13 which is welded to the outer end of a rear portion of the trailing arm 10 . Also, the inner end of the rear portion of the trailing arm 10 has washers 15 which support the bottom end of a suspension spring.
- the torsion beam 11 has an angular U-shaped cross-section which opens towards the front of the vehicle body.
- a gusset 11 b is welded w 1 such that it covers notch 11 a formed in the rear side edge of the end of the torsion beam.
- the edge of torsion beam 11 including gusset 11 b is fitted to and welded w 2 to the vertical surface of the trailing arm 10 .
- the trailing arm 10 is a hollow integral member made by welding w 3 together an upper half 21 and a lower half 22 which are press-formed from metal plates, and a spring washer 15 is provided in the upper half 21 .
- the end face 10 a of the trailing arm 10 to which the spindle support plate 13 is secured has a closed cross-section.
- the spindle support plate 13 is a substantially rectangular plate member, four bent flanges 13 b - 13 e are formed at the four corners of the flat body 13 a, and clamp sections 13 f - 13 i are formed to project vertically and laterally.
- the four bent flanges 13 b - 13 e of the spindle support plate 13 are fitted to the outer periphery of the end of the trailing arm 10 , and are welded w 4 to the outer periphery of the end of trailing arm 10 .
- the four clamps 13 f - 13 i are clamped in order to determine the position of the spindle support plate 13 with regard to the trailing arm 10 , and welded in this condition, so that welding precision can be improved.
- bent flanges 13 b - 13 e are provided at the four corners of spindle support plate 13 , resulting in an effective positioning of the spindle support plate 13 with regard to the trailing arm 10 .
- the outer periphery of the end of the trailing arm 10 and the inner surfaces of the bent flanges 13 b - 13 e of the spindle support plate 13 are parallel with each other in section A where they overlap, forming a small gap ⁇ .
- the projection height h of the bent flanges 13 b - 13 e is not more than twice the thickness t of the wall thickness of the spindle support plate 13 (h ⁇ 2t), so that the shapes of the bent flanges of 13 b - 13 e are secured to be stable and parallel within the region, and at the same time, the bonding rigidity can be ensured by welding w 4 at the vicinity of each corner.
- Each bent section B of the inner surfaces of the bent flanges 13 b - 13 e is made to have an extremely small curvature radius ( ⁇ 1 mm), and there is a small gap ⁇ between the end surface 10 a of the trailing arm 10 and the inner surface of spindle support plate 13 .
- the mounting angle of the spindle support plate 13 can be adjusted freely to some extent with regard to the trailing arm 10 , and the positioning of the spindle support plate 13 in welding w 4 the spindle support plate 13 to the trailing arm 10 is facilitated, whereby the welding precision can be further improved.
- a spindle support hole 13 m is burring-formed in the center of the body 13 a of the spindle support plate 13 .
- the spindle 14 has a large diameter section 14 b leading to an annular projection 14 a formed in the longitudinal center, a taper section 14 c and a small radius section 14 d.
- the spindle support hole 13 m is enlarged by the taper section 14 c and the large diameter section 14 b is press-fitted into the spindle support hole 13 m, and in the end, the projection 14 a abuts against the body 13 a of the spindle support plate 13 .
- the small diameter section 14 d at the end of spindle 14 a passes through within and projects out of the opening 21 a formed in the upper half 21 of the trailing arm 10 , and is secured by welding w 5 .
- the bent flanges 13 b - 13 e are formed in the outer periphery of the spindle support plate 13 , and these bent flanges 13 b - 13 e are fitted and welded to the outer periphery of the end of trailing arm 10 , so that even if the wall thickness of the spindle support plate 13 is reduced from the conventional 10 mm or more to around 5 mm to 7 mm in order to reduce the weight, the body 13 a of the spindle support plate 13 can be prevented from warping due to the heat of welding w 4 .
- the spindle support plate 13 is directly connected to the end of the trailing arm 10 without use of a bracket, the offset between the axle line of the spindle 14 and the major cross-section of the trailing arm 10 is reduced, and the rigidity of the trailing arm 10 and spindle 14 assembly is enhanced.
- the four bent flanges 13 b - 13 e are formed at the four corners of the spindle support plate 13 , but a single bent flange may be formed around the whole outer periphery of the spindle support plate 13 and the number other than four of bent flanges may be formed. Also, the bonding strength can be further increased if the tip end of the spindle support hole 13 m and the large diameter section 14 b of the spindle 14 are welded together.
Abstract
Description
- 1. Field of the Invention
- The present invention relates to a torsion beam suspension comprising: vertically pivotable left and right trailing arms extending in a longitudinal direction of a vehicle body; a torsion beam extending in a lateral direction of the vehicle body, the opposite ends of which are connected to the left and right trailing arms; a spindle support plate welded to each of the left and right trailing arms; and a spindle fixed to the spindle support plate so as to axially support a wheel.
- 2. Description of the Related Art
- A conventional torsion beam suspension is known from Japanese Patent Application Laid-open No. 2000-94917.
- In the conventional torsion beam suspension, a trailing arm is a hollow member made by combining and integrally welding press-formed upper and lower plates, and a bracket formed from an angular U-shaped metal plate is welded to the trailing arm to secure a spindle support plate which supports a wheel.
- However, the above-mentioned conventional design has a problem in that the spindle axle line and the trailing arm major cross-section are largely offset with the angular U-shaped bracket disposed therebetween, so that the bracket must have a wall thick enough to reliably support a load from the wheel, resulting in an increased weight.
- Therefore, it is conceivable that the angular U-shaped bracket is eliminated, a spindle support plate is welded to an end of the trailing arm, and the spindle is blot-fixed to the spindle support plate through a mounting flange integral with the spindle. In doing so, not only is the weight reduced by eliminating the heavy bracket, but it also becomes possible to bring the spindle axle line and the trailing arm major cross-section closer to each other, resulting in an advantageous strength.
- However, in reality, when the trailing arm end is welded to the spindle support plate, the spindle mounting surface of the spindle support plate may be warped by the heat of welding. In order to prevent this thermal warping, it is necessary to make the spindle support plate sufficiently thick (for instance, over 10 mm), so that the total thickness of the spindle support plate and the mounting flange (for instance, 10 mm thick) integral with the spindle which is connected to the spindle support plate, becomes over 20 mm, disadvantageously resulting in no reduction in weight. Moreover, there is also a problem that welding property is deteriorated due to a large difference in thickness of the trailing arm having a small wall thickness and the spindle support plate having a large wall thickness.
- In order to solve the problems of thermal warp and weight, the spindle support plate can be machined to be flat and thinner after welding the spindle support plate to the trailing arm end. However, in this case, because the spindle axle line is the reference for the surface cut, it is necessary to rotate the whole trailing arm in conducting the surface cut, so that machining becomes very complicated and costly.
- It is also conceivable to eliminate the spindle support plate, and weld the spindle-mounting flange assembly directly to the trailing arm, but it is still necessary that the mounting flange thickness be for
instance 13 mm or more, in order to solve the problem of thermal warp. Therefore, a weight increase is unavoidable. - Accordingly, an object of the present invention is to reduce weight by reducing the wall thickness of the spindle support plate which is directly welded to the end of the trailing arm, and to effectively prevent thermal warp which accompanies welding.
- In order to achieve the above object, according to a first feature of the invention, a torsion beam suspension comprising: vertically pivotable left and right trailing arms extending in a longitudinal direction of a vehicle body; a torsion beam extending in a lateral direction of the vehicle body, the opposite ends of which are connected to the left and right trailing arms; a spindle support plate welded to each of the left and right trailing arms; and a spindle fixed to the spindle support plate so as to axially support a wheel, wherein a bent flange is formed around an outer periphery of a body of the spindle support plate and is fitted around an outer periphery of an end of the trailing arm, the bent flange being welded to the trailing arm.
- With this arrangement, because the bent flange is formed around the outer periphery of the body of the spindle support plate and is fitted around the outer periphery of the end of the trailing arm, the bent flange being welded to the trailing arm, the heat from welding is blocked by the bent flange of the spindle support plate, to thereby prevent the heat from reaching the body. Therefore, thermal warp of the body of the spindle support plate which retains the spindle is prevented, and not only can the spindle mounting precision be improved without cutting the spindle support plate surface, but the support plate thickness can be reduced to reduce the weight. Moreover, welding property is improved because the difference in wall thickness compared with the trailing arm is reduced.
- According to a second feature of the invention, in addition to the arrangement of the first feature, a spindle support hole is formed in the body of the spindle support plate by burring, and the spindle is press-fitted into the spindle support hole.
- With this arrangement, the spindle support hole can be formed in the spindle support plate by burring because the spindle support plate is made thinner. As a result, the spindle can be retained by press-fitting it into the burring-formed spindle support hole without forming a spindle-mounting flange assembly to retain the spindle support plate, that is, the spindle weight can be reduced by the weight of the eliminated mounting flange.
- Furthermore, according to a third feature of the invention, in addition to the arrangement of the second feature, a tip end of the spindle press-fitted into the spindle support hole passes through within the trailing arm and projects out of the trailing arm, a projecting portion of the spindle being welded to the trailing arm.
- With this arrangement, because the tip end of the spindle press-fitted into the spindle support hole passes through within the trailing arm and projects out of the trailing arm, a projecting portion of the spindle being welded to the trailing arm, the heat of welding does not affect the spindle support plate, thereby firmly connect the spindle to the trailing arm.
- FIG. 1 is a front plan view of the left half of a torsion beam suspension.
- FIG. 2 is an enlarged cross-sectional view taken along line2-2 in FIG. 1.
- FIG. 3 is a cross-sectional view taken along line3-3 in FIG. 1.
- FIG. 4 is a cross-sectional view taken along line4-4 in FIG. 2.
- FIG. 5 is a view taken from arrow5 in FIG. 3.
- The present invention will be described with reference to a preferred embodiment shown in the attached drawings.
- FIG. 1 is a front plan view of the left half of a torsion beam suspension for rear wheels of an automobile, and the right half of the torsion beam suspension has a construction symmetrical with that of left half with respect to the longitudinal centerline of the vehicle. The torsion beam suspension has left and right trailing
arms torsion beam 11 which extends in the lateral direction of the vehicle body to link to the left and right trailingarms trailing arm 10 is welded to a tubulartrailing arm support 12. Thetrailing arm 10 is vertically pivotably supported on the vehicle body via a rubber bushing joint (not shown) accommodated in the trailingarm support 12. A rear wheel W is rotatably supported on thespindle 14 fixed to thespindle support plate 13 which is welded to the outer end of a rear portion of thetrailing arm 10. Also, the inner end of the rear portion of the trailingarm 10 haswashers 15 which support the bottom end of a suspension spring. - The
torsion beam 11 has an angular U-shaped cross-section which opens towards the front of the vehicle body. Agusset 11 b is welded w1 such that it coversnotch 11 a formed in the rear side edge of the end of the torsion beam. The edge oftorsion beam 11 includinggusset 11 b is fitted to and welded w2 to the vertical surface of the trailingarm 10. - The
trailing arm 10 is a hollow integral member made by welding w3 together anupper half 21 and alower half 22 which are press-formed from metal plates, and aspring washer 15 is provided in theupper half 21. The end face 10 a of thetrailing arm 10 to which thespindle support plate 13 is secured has a closed cross-section. - The
spindle support plate 13 is a substantially rectangular plate member, fourbent flanges 13 b-13 e are formed at the four corners of theflat body 13 a, andclamp sections 13 f-13 i are formed to project vertically and laterally. The fourbent flanges 13 b-13 e of thespindle support plate 13 are fitted to the outer periphery of the end of thetrailing arm 10, and are welded w4 to the outer periphery of the end of trailingarm 10. At that time, the fourclamps 13 f-13 i are clamped in order to determine the position of thespindle support plate 13 with regard to thetrailing arm 10, and welded in this condition, so that welding precision can be improved. In particular,bent flanges 13 b-13 e are provided at the four corners ofspindle support plate 13, resulting in an effective positioning of thespindle support plate 13 with regard to thetrailing arm 10. - As is enlarged in the circle in FIG. 4, the outer periphery of the end of the
trailing arm 10 and the inner surfaces of thebent flanges 13 b-13 e of thespindle support plate 13 are parallel with each other in section A where they overlap, forming a small gap α. The projection height h of thebent flanges 13 b-13 e is not more than twice the thickness t of the wall thickness of the spindle support plate 13 (h≦2t), so that the shapes of the bent flanges of 13 b-13 e are secured to be stable and parallel within the region, and at the same time, the bonding rigidity can be ensured by welding w4 at the vicinity of each corner. Each bent section B of the inner surfaces of thebent flanges 13 b-13 e is made to have an extremely small curvature radius (<1 mm), and there is a small gap β between theend surface 10 a of thetrailing arm 10 and the inner surface ofspindle support plate 13. - In this manner, the mounting angle of the
spindle support plate 13 can be adjusted freely to some extent with regard to thetrailing arm 10, and the positioning of thespindle support plate 13 in welding w4 thespindle support plate 13 to thetrailing arm 10 is facilitated, whereby the welding precision can be further improved. - Four
weld nuts 16 are secured on the inner surface of thespindle support plate 13, and a back plate of a braking device (not shown) which is mounted to the outer surface of thespindle support plate 13 is secured by tightening bolts into theseweld nuts 16. Twoholes upper clamp 13 e in order to mount ABS equipment. - A
spindle support hole 13 m is burring-formed in the center of thebody 13 a of thespindle support plate 13. Thespindle 14 has alarge diameter section 14 b leading to anannular projection 14 a formed in the longitudinal center, ataper section 14 c and asmall radius section 14 d. Thespindle support hole 13 m is enlarged by thetaper section 14 c and thelarge diameter section 14 b is press-fitted into thespindle support hole 13 m, and in the end, theprojection 14 a abuts against thebody 13 a of thespindle support plate 13. At this time, thesmall diameter section 14 d at the end ofspindle 14 a passes through within and projects out of theopening 21 a formed in theupper half 21 of thetrailing arm 10, and is secured by welding w5. - As described above, the
bent flanges 13 b-13 e are formed in the outer periphery of thespindle support plate 13, and thesebent flanges 13 b-13 e are fitted and welded to the outer periphery of the end of trailingarm 10, so that even if the wall thickness of thespindle support plate 13 is reduced from the conventional 10 mm or more to around 5 mm to 7 mm in order to reduce the weight, thebody 13 a of thespindle support plate 13 can be prevented from warping due to the heat of welding w4. Therefore, it is unnecessary to perform machining on thesurface 13 a of thespindle support plate 13 after welding w4 in order to eliminate the effects of warping, which contributes to a reduction in the processing costs. Furthermore, by reducing the wall thickness of thespindle support plate 13, the difference in thickness between thespindle support plate 13 and thetrailing arm 10 is decreased, whereby degradation of welding property can be prevented. - Also, because the
spindle support plate 13 is directly connected to the end of thetrailing arm 10 without use of a bracket, the offset between the axle line of thespindle 14 and the major cross-section of thetrailing arm 10 is reduced, and the rigidity of thetrailing arm 10 andspindle 14 assembly is enhanced. - By reducing the wall thickness of the
spindle support plate 13, it becomes possible to form thespindle support hole 13 m in thespindle support plate 13 by burring. This is because if thespindle support plate 13 is too thick, the material expansion rate becomes too large during the burring, thereby easily generating cracks. Therefore, it becomes possible to retain thespindle 14 by press-fitting it into thespindle support hole 13 m formed by burring in thespindle support plate 13 without providing a mounting flange to thespindle 14. That is, a mounting flange can be eliminated from thespindle 14, contributing to a reduction in weight. - Also, because the tip end of the
spindle 14 which is press-fitted into thespindle support hole 13 m, is then passed through the opening 21 a into and out of the trailingarm 10, and welded w5 into place, mounting rigidity of thespindle 14 and the trailingarm 10 with regard to thespindle support plate 13 can be dramatically enhanced, which can contribute to increases in camber rigidity and suspension toe rigidity. The weld site w5 is sufficiently distanced from thespindle support plate 13, so that there is no possibility that the heat from welding causes thermal warping of thespindle support plate 13, - The preferred embodiment of the present invention has been described in detail above, but various modifications in design may be made thereto without deviating from the scope and spirit of the present invention.
- For instance, in the preferred embodiment, the four
bent flanges 13 b-13 e are formed at the four corners of thespindle support plate 13, but a single bent flange may be formed around the whole outer periphery of thespindle support plate 13 and the number other than four of bent flanges may be formed. Also, the bonding strength can be further increased if the tip end of thespindle support hole 13 m and thelarge diameter section 14 b of thespindle 14 are welded together.
Claims (3)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JP2002-199449 | 2002-07-09 | ||
JP2002199449A JP4093548B2 (en) | 2002-07-09 | 2002-07-09 | Torsion beam suspension |
Publications (2)
Publication Number | Publication Date |
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US20040007846A1 true US20040007846A1 (en) | 2004-01-15 |
US6935646B2 US6935646B2 (en) | 2005-08-30 |
Family
ID=29728430
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/313,952 Expired - Fee Related US6935646B2 (en) | 2002-07-09 | 2002-12-06 | Torsion beam suspension |
Country Status (4)
Country | Link |
---|---|
US (1) | US6935646B2 (en) |
EP (1) | EP1380455B1 (en) |
JP (1) | JP4093548B2 (en) |
CN (1) | CN1270910C (en) |
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US20070126200A1 (en) * | 2005-12-05 | 2007-06-07 | Honda Motor Co., Ltd. | Torsion beam suspension |
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US20070290474A1 (en) * | 2005-03-04 | 2007-12-20 | Mitsuru Inoue | Torsion Beam Suspension |
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US11104200B2 (en) * | 2018-08-22 | 2021-08-31 | Benteler Automobiltechnik Gmbh | Method for producing an axle component |
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CN109094322B (en) * | 2018-08-08 | 2020-07-07 | 吉利汽车研究院(宁波)有限公司 | Torsion beam structure |
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JP3551039B2 (en) | 1998-09-25 | 2004-08-04 | トヨタ自動車株式会社 | Torsion beam suspension |
JP3605534B2 (en) | 1999-10-21 | 2004-12-22 | 本田技研工業株式会社 | Torsion beam suspension |
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- 2002-07-09 JP JP2002199449A patent/JP4093548B2/en not_active Expired - Fee Related
- 2002-12-06 US US10/313,952 patent/US6935646B2/en not_active Expired - Fee Related
- 2002-12-10 EP EP02258502A patent/EP1380455B1/en not_active Expired - Fee Related
- 2002-12-11 CN CN02155914.7A patent/CN1270910C/en not_active Expired - Fee Related
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US4165098A (en) * | 1977-11-28 | 1979-08-21 | Chrysler Corporation | Rear suspension apparatus for a motor vehicle |
US5507518A (en) * | 1993-12-24 | 1996-04-16 | Yorozu Corporation | Torsion beam type suspension and method for production thereof |
US6059314A (en) * | 1996-11-27 | 2000-05-09 | Benteler Ag | Method of manufacturing a composite control arm shaft for motor vehicles and composite control arm shaft |
US6152468A (en) * | 1997-11-14 | 2000-11-28 | Benteler Ag | Composite suspension control arm shaft for motor vehicles |
Cited By (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20100201182A1 (en) * | 2005-01-14 | 2010-08-12 | Michael John Gottschalk | Continuous radius axle and fabricated spindle assembly |
US7878516B2 (en) * | 2005-01-14 | 2011-02-01 | Michael John Gottschalk | Continuous radius axle and fabricated spindle assembly |
US20070290474A1 (en) * | 2005-03-04 | 2007-12-20 | Mitsuru Inoue | Torsion Beam Suspension |
US7556272B2 (en) * | 2005-09-06 | 2009-07-07 | Gm Global Technology Operations, Inc. | Twist axle suspensions |
US20070052194A1 (en) * | 2005-09-06 | 2007-03-08 | Jacek Marchel | Twist axle suspensions |
US20070246904A1 (en) * | 2005-09-12 | 2007-10-25 | Satoshi Murata | Torsion-Beam-Type Suspension Apparatus |
US20070126200A1 (en) * | 2005-12-05 | 2007-06-07 | Honda Motor Co., Ltd. | Torsion beam suspension |
US7871093B2 (en) * | 2005-12-05 | 2011-01-18 | Honda Motor Co., Ltd. | Torsion beam suspension |
CN104139678A (en) * | 2007-03-01 | 2014-11-12 | 丰田自动车株式会社 | Torsion beam type suspension |
EP2305492A1 (en) * | 2009-10-02 | 2011-04-06 | Benteler Automobiltechnik GmbH | Twist beam axle |
US10543728B2 (en) | 2014-10-03 | 2020-01-28 | F-Tech Inc. | End plate of suspension member |
CN106240276A (en) * | 2016-08-24 | 2016-12-21 | 奇瑞商用车(安徽)有限公司 | A kind of rear torsion beam welding bridging arrangement |
CN108688421A (en) * | 2017-04-04 | 2018-10-23 | 株式会社 F.泰克 | Rear suspension towing arm |
US11383574B2 (en) * | 2018-03-29 | 2022-07-12 | Magna International Inc. | Vehicle twist axle assembly |
US11104200B2 (en) * | 2018-08-22 | 2021-08-31 | Benteler Automobiltechnik Gmbh | Method for producing an axle component |
WO2024052481A1 (en) * | 2022-09-09 | 2024-03-14 | Trailer Dynamics Gmbh | Chassis for a utility vehicle |
Also Published As
Publication number | Publication date |
---|---|
CN1467101A (en) | 2004-01-14 |
JP2004042690A (en) | 2004-02-12 |
EP1380455A2 (en) | 2004-01-14 |
CN1270910C (en) | 2006-08-23 |
EP1380455A3 (en) | 2004-07-14 |
US6935646B2 (en) | 2005-08-30 |
EP1380455B1 (en) | 2011-02-16 |
JP4093548B2 (en) | 2008-06-04 |
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